Inertia operated control device



Oct. 30, 1951 R. J. BUSH INEJRTIA OPERATED CONTROL DEVICE Filed Aug.

2 SHEETSSHEET l m 3 M mu 6 m m 1% m. R M m F I M K LE Q liillmiliiil -i ii}- 1 m rim 9 m o. 1 Q Q m Q v m m m w h ATTORNEY Oct. 30, 1951 R. J. BUSH INERTIA OPERATED CONTROL DEVICE 2 SHEETS HEET 2 Aug. 31

ll )1 4 l In.

Q INVENTOR- R fl JBU Y ATTORNEY Patented Oct. 30, 1951 INERTIA OPERATED CONTROL DEVICE Rankin J. Bush, Greensburg, Pa., assignor to Westinghouse Air Brake Company, a corporation of Pennsylvania Application August 31, 1949, Serial No. 113,352

- v11 Claims.

This invention relates to an inertia operated control device for control of the brakes of vehicles and, more particularly, to an improved inertia operated control device of the rotary type for controlling the application of brakes on the landing wheels of airplanes in such a manner as to prevent sliding of the landing wheels due to brake application.

As is well known, airplanes necessarily travel at relatively high speeds in landing. Consequently the landing wheels of an airplane are accelerated very rapidly either from a non-rotative condition or. an initially low rotative speed (if the landing wheel tires are provided with accelcrating flaps or other means for that purpose) at the instant of contact of the wheel tires with the runway. For a certain time after the first contact of the landing wheel tires with the runway, the airplane mayflibounce vertically inre peated succession due to the unevenness of the runway or the varying lift on the wings of the airplane, thus producing a wide variation of the force pressing the wheels to the ground and in some cases even lifting the wheels clear of the runway.

It will thus be seen that for a certain interval of time after the first instant that the landing wheels touch the runway or ground, it is not practical for the pilot of the airplane to effect an application of the brakes on the wheels because during the interval of light load or absence of load on the wheels the degree of brake application established inevitably effects locking of the wheels. Thus, recontact of the wheels as the airplanesettles to the ground causes slipping or sliding of the wheel tires. Slipping or sliding of the wheel tires is objectionable in that it causes rapid wearing away of the tire surface which ultimately destroys the tire, and in some cases causes tire blowouts resulting in upsets and damage to the airplane.

As used herein, the terms slipping and sliding applied to the landing wheels of an airplane are not synonymous. The term slip and its variations, as employed herein, identify a rotating condition of the landing wheel in contact with the ground in which the peripheral speed of the wheel at a given instant varies from the linear or ground speed of the airplane. The term slide and its variations, as used herein, refers-to the dragging of a landing wheel along the runway or ground in contact therewith while the wheel is locked or not rotating.

In order to avoid, as much as possible, the undesired slipping or sliding of. the wheel ,tires a on landing, the pilot of an airplane customarily delays effecting a brake application for a certain interval oftime-sometimes as much as six seconds'following the initial contact of the landingwheels with the ground. Where the length; ofthe runways onalanding field is sufiicient, the delay in-eliecting the brake application is not necessarily disadvantageous. However, where the runway is. unusually short it is quite difficult and sometimes impracticable to land an airplane requiring a long stopping distance, particularly in the case of larger airplanes having. extra high landing speeds.

:It is desirable, 1 therefore, to provide means whereby to minimize as much as possible, the delay period required following the instant ofinitial contact of the landing wheels of the airplane with the runway or ground, before a brake application on'the landing wheels may be safely ef-, fected. It has previously been proposed, therefore, to employ rotary inertia devices which rec ognize the slipping condition of the landing wheels and which'operate to automatically effect a release of a brake application on the wheels, initiated by the pilot of the plane, thereby to prevent the locking of the landing wheels and the sliding thereof, so as to enable the brake ap plication to be effected on the landing wheels as rapidly as possible after the first contact of the wheels with the runway. 1

One type of rotary inertia device heretofore proposed for this purpose is shown and described and claimed in the copending application of Charles W. Berkoben and Rankin J. Bush, Serial No. 51,546, filed September 28, 1948 and assigned to the assignee of the present application. This type includes a friction clutch in the driving mechanism for the inertia element or mass of the device, which clutch device serves to prevent damage to the parts of the inertia device, due to forces generated upon sudden acceleration or deceleration of landing wheels.

The single friction clutch type of drive for the inertia element of a rotary inertia device employed for the control of airplane brakes is sub-' ject to the disadvantage that if the frictional force exerted by the clutch is suflicient to effect rapid acceleration of the inertia element back toward a wheel speed corresponding to the ground speed of the airplane at a rapid rate, then an excessively rapid rate of deceleration of the. inertia element during the decelerationportion of the slipping cycle or period occurs which mayv result in the undesired premature reapplication of the brakes during the wheel slip period. On,the

other hand, if the frictional force exerted by the single clutch is light enough so as not to cause dn unduly rapid rate of deceleration of the inei tia element during the dece'lratin portion of the slipping period of the landing wheel, the acceleratifin' of the inertia element back toward a wheel speed corresponding to the ground speed of the airplane is lindiily delayed and, consequently, the feapplic'ation" of the brakes following return of the landing wheel to the ground speed of the airplane is unduly delayed.

Where a single clutch type of drive is employed, therefore, it is necessary to adopt a compromise degree of frictional force. Consequently, due to the compromise degree of frictional iorce'exerted by the single clutch, reapplication of the brakes under the control of the inertia device is some: what delayed followin the restoration of a slipping landing wheel to a speed corresponding to the ground speed of the airplane, thus undesirably lengthening the stopping distance of the plane.

It is accordingly one object of my. present invention to provide" an improved rotary inertia device'for the control of the brakes on the landing wheels of airplanes, characterized by a type of drive for the inertia element of the device which functions to materially reduce the delay, in-. herently caused by'heretofore" known rotary inei'tia. devices, following the restoration of a slipping landing wheel to the ground speed of the airplane before reapplication of the brakes on the landing wheel may be effected, while retaining theadvantage of preventing damage to parts of the inertia device due to forces generated upon rapid acceleration or deceleration of the landm g wheel's.

"Anotherand more specific object of my invention'is to provide an improved rotary inertia'device, of the type mentioned in the foregoing object', characterized by a multiple clutch type of drive arrangement for the inertia element which iilnctions automatically to cause deceleration of thinertia eleinent at a relatively slow rate durihg the deceleration part of the wheel slip period and which also causes acceleration of the" inertia element'at a rapid rate during the acceleration portion'of the wheel slip period. An6ther object of my invention is to provide an improved rotary inertia device, of the type mentioned in the foregoing objects, characterized wanna-parathion type of-drive for the inertia element in which only one clutch is efiective durlag the deceleration portion of the slippin period 6f 'the'landing wheel and in'which both clutch devices are effective during the acceleration portion of the slipping period of the landin'gwheel.

Other and more detailed objects of myinvention' will appear in the following description thereof when read in conjunction with the accompanying drawings, wherein,

Fig. 1 is a fragmental horizontal cross-section view of a conventional airplane wheel assemblage, showing one embodiment vof my improved rotary inertia device applied thereto,

Fig. 2 is an enlarged fragmental cross-sectional view, takensubstantially on the line 2'-2-, of Fig.1,

Fig; 3 is an enlarged cross-sectional view, taken on the line 33 of Fig. 1, showing details of my improved rotary inertia operated device, Fig. 4 is a"sectional view,'tal 1en onthe line fl- L of- Fig. 3, with parts broken away for clarity, showing further construction details. Referring to' Fig. 1-, th'airplane wheel as- 4 semblage shown comprises a wheel I, the usual pneumatic tire for which is now shown, which wheel is rotatively mounted in conventional manner on a tubular non-rotative axle 2 through the medium of suitable bearings 3 and 4 disposed respectively at opposite ends of the wheel hub.

The brake mechanism for braking wheel I comprises a cylindrical bra-l te drum 5 attached at one end, as by securing bolts 6, to the inner web of the landing Wheel, an annular segmented brake shoe I disposed within and surrounded by the drum and. an expansible and contractable brake'tube 8 for operating the shoe 1.

*The annular. brake shoe 1 is supported and uided, for radial movement into and out of engagement with the inner surface of the brake granup th periphery of an annular support member Q of dish-shape, the member 9 having a central hub portion through which the axle 2 extends and being attached to a radially extending flange ID on the axle 2, as by a plurality of bolts I I, only one of which is shown.

The annular brake tube 8 is supported by the member 9 inconcentric relation within the ane nular brake. shoe 1., the. brake tube being provided with a suitable fittin l2 whereby a pipe i3 is connected to the tubefor the purpose of supply= ing fluid under pressure to the interior of the tube andreleasing it therefrom.

Suitable release springs, illustrated as curved leaf springs 14, are interposed between the sup; port member 9 and the segments of the annular brake shoe! in such a manneras to bias the brake shoe segments normally radially inwardly to a release position out of engagement with the inner surface of the brake. drum 5. Introduction of fluid at sumcient pressure to the interior of the brake tube 3,. expands the. tube. and applies a radial pressure uniformly on .the segments, of the brake shoe E to. thereby efiect engagement thereof with the brake drum 5, in opposition to the yielding force. of the springs 14,

According to my invention, the brake control apparatus provided comprises my improved rotary inertia device l5, and a so-called release valve device l6 controlled by the rotary inertia device 115. and eifectiveito control the supply of fluid under pressure to or the release of fluid under pressure. from the pipe, L3 leading to. the brake tube. 8:

The rotary inertia device licomprises a suitable casing ll, generally cylindrical in appearance, having a flange. at one end whereby to secure the device to the outer end of the hub of the landing wheel I. Various expedients maybe resorted to in securing the device l5 to the wheel I, depending uponthe type of the landing wheel and; the construction thereof. In the typf of landin wheel shown, however, the meansprovided for securing 'thecas ing ll to the hub of the landing wheel lso as to rotate therewith, includes a ring it secured in the .bore {9; in which he m or i i ihabea ics a c iv d as by a split looliring 20, the flange at one end of he. asin ll einfe. tached o he n 8 s by ur t ip-Q 5 or. s r 1- 1 mechan sm c 11 when ner ia deviceilii c mpr es n. ner a em n or ma shown in "Eh? m. ii-w e a bl m unt d iea bear g ,41 n. ha t 23,-. Shah s rotatably mounted; at one end in'the casingi'l, as by a'bearing '25 in an inner wall 2 6- of the casing, and at the other end by a bearing Al-car;- ried in a suitable recess on the inner face off'a removable cover 2 8,'whic h is adapted tobese; cured to and close theouter end, of the casing l-l',

A tation of the casing The mechanism'for driving :the' fiyewheel .22 comprises an orbit gear 29 having teethon the inner surface thereof and machined to a smooth surface. on the outer periphery thereof, the orbit gear being contained in close-fitting relation a suitable smooth bore 30 in thecasing and capable of rotation in the bore with respect-.tothe casing.

The orbit gear 29 is frictionally held in the casing for rotation therewith by a multiple clutch arrangement constituting a special feature of my invention and which will be presently described.

A driving connection between the orbit gear and the fiy-wheel 22 is provided through the medium of a plurality of planetary 'gears 3| shown as three in number, that mesh externally with the orbit gear and internally with a sun gear 32 formed on or attached to the projecting end of the hub of the fiy-wheel 22. I

The planetary gears 3| are mounted for rotation in the same plane, as by suitable ball bearing races 33, on bolts 34 attached inequal angularly spaced relation and equidistant from the axis of the shaft 23 to a radially extending disclike flange 35 formed integrally with the shaft 23.

The inner end of the shaft 23 projects out through the wall 26 and a disc 36 is secured thereto for rotation therewith as by ,a key and keyway. The disc 36 has a plurality of pins 31, shown as two in number, disposed in diametrical relation for engaging in suitable holes 38 of a disc-like yoke 39 attached to one end of an operating rod 40.

The multiple clutch arrangement, previously mentioned, for holding the orbit gear 29 .so as to rotate with the casing comprises, according, to my invention, a friction or clutch ring 4| interposed at the base of the bore 39 between a cooperating clutch face formed on the wall 26 and the adjacent cooperating side of the orbit gear 29.

The multiple clutch arrangement further comprises an annular clutch member 42,;disposed on the side of the orbit gear 29 opposite to clutch ring 4| and having attached thereto a friction or clutch ring 43 for engaging the adjacentside of the orbit gear 29. One or more spring members 44 (only one being shown) serve to exert an axial force through the medium of a thrust bearing 45 on the clutch member 42 whereby to effect the gripping engagement of the orbit "gear 29 between the clutch rings 4! and 43, and at the same time exert a force pressing the friction ring 4| into frictional contact with the clutch face formed on the wall 26 of the casing Although only one spring 44 is shown, it will be understood that one or more of such spring members may be employed, depending upon the force required to be exertedthereby. As shown, the spring member 44 is in the form of a central ring portion from which radiate in spoke-like relation a plurality of resilient fingers, the tip ends of which engage the outer bearing ring'or race of the thrust bearing 45. The central ring portion of the spring member 44 is supported on a central projection or shoulder 46 formed on the inner face of the cover 28 in surrounding relation to the bearing 21.

According to my invention, I provide an arrangement for automatically locking and unlock- ,ing the clutch member 42 to the casing H whereby selectively to cause exertion of a frictional force by the clutch ring 43 on the orbit gear 29 or the removal of such frictional force uponroe will be seen particularly in Fig. 4, the mech;

anism which I provide'for selectively locking and unlocking the clutch member 42 with respect to the casing comprises a plurality of latch members or latches 41, illustrated as two in number, pivotallycarried on so-called latch covers 48 disposed in substantially diametrical relation on opposite sides'of casing Each latch member 4141s biased by a spiral spring 49 in such a manner'as to engage the outer peripheral surface of; the clutch member 42. The latch covers 48 are 'removably secured to the casing I! as by a, plurality of screws 50 and may be reversed in position to suitably orient the latch members 41 with respect to the head end of the airplane so as to operate similarly for wheels on the left or right side of the airplane.

The outer periphery of the clutch member 42 is provided with a clutch surface illustrated in the form of a plurality of projecting lugs 5| equally spaced around the periphery of the clutch member against which lugs the latches 41 are biased; In the position of the latches 41 shown in -Fig. 4, rotation of the casing in a counterclockwise direction will cause one or both of the latches to drop down into the recess between successive lugs 5| and engage the side surface of the lugs, toprovide a positive lock whereby the rotation of the casing effects a corresponding positive rotation of the clucth member 42. Con versely, upon rotation of the casing 11 in a clockwise direction, as .seen in Fig. 4, the latches 41 raise asthey strike the lugs 5| and consequently free rotation of the casing IT with respect to the clutch member 42 is permitted. 7

g It will thus be seen that, for one direction of rotation of the casing IT with respect to the clutch member 42, the clutch member is locked for rotation with the casing and consequently, renders the clutch ring 43 effective to grip the orbit gear 29. Consequently, it will be seen that under such circumstances a high degree of driving torque may be exerted to drive the orbit gear in synchronism with the casing because both the clutch rings 4| and 43 will be effective to grip the orbit gear 29. It will also be seen that when the casing rotates in the opposite direction with respect to the clutch member 42, th clutch member and clutch ring 43 rotate free of the casing except for the negligible friction in the thrust bearing 45. Consequently, in such case, only the clutchring 4| is effective to transmit a driving torque from the casing to the orbit gear 29fthere- .by limiting the driving torque applied to the orbit gear 29 to a relatively low value compared to that to which th driving torque is limited when both clutch rings 4| and 43 are effective.

Itwill be apparent that when the casing I! is rotatively accelerated, the orbit gear 29 exerts a driving torque to accelerate the fly-wheel 22 to to a degree limited by the frictional force of both clutch rings 4| and 43. Due to the reaction of the forces exerted on the planetary gears 3| upon rotative acceleration of the casing H, the flange shifts rotatively in one direction out of a certain normal non-rotative position in which it is held, as explained hereinafter, to thereby efiect rotation of the operating rod correspondingly.

It willalso be seen that upon rotativ decelerationof thecasing II, the reactive forces exerted on the planetary gears 3| due to the inertia effect of the flywheel 22 causes the flange 35 to be ro- 7? Eurther peration of the rotary inertia device |5 amine will be made apparent in the subsequentdescrlp tion ofthe entire apparatus.

Referring to Fig. 2, there is shown the opera, tive connection between th operatiz-ig rod 40 and the operating lever 52 of the release valvedevice l6, whereby rotation of theoperating rod 40 effects operation of the release valve. It will be seen that operating rod 40 extends coaxially within the tubular axle -2 from the rotary inertia device l5 and has secured thereto, for'the purpose mentioned, a rocker arm 53 also within-the tubular axle 2, the end of the rocker arm having one end of a'connectinglink or link rod -54 con: nected thereto as by a pin 55 and theopposite end of the link-rod 5t being pivotally connected as by a pin 55 to the outer end of the operating lever 52. Th release valve I6 is supported on a suitable bracket on the outside of the axle 2, and thus a suitable slot orpassage 5 1 is provided in the wall of the axle through which the link rod 54 extends.

The release valve 46, as shown in Fig. 2,"eom prises a casing 53 having a central bore 59-therein, containing a piston valve device 60-. Piston valve 66 comprises an annular piston =61 operative in the bore 59 and a piston valve 62'oper-a-tive in a bore 63 'coaxially related to thebore 59-andof smaller diameter. Piston 5i and piston valve 62 are preferably formed at opposite ends of a tubular member which is closed at the end at which the piston valve 62 is located and open'at the end at which the piston BI is located. A coilspring 64 interposed between the'closed-end of the tubular member and the inner fac of a cover 65, closing the open end ofbore 59,-yieldingly biases the piston valve device to to a position in which the piston valve 62'seats on an annular rib seat to close a port 61' through which a connection is established, as explained hereinafter, between an exhaust passagetfl and a passage 69. Pipe 13 leading to the brake tube 8is suitably connected to the passage 89; a 3 Formed within the berets between the piston 6| andpiston-valve 62 is-an annular chamber Tilto which is connected a fluid pressure supply pipe H. A brake controlling valve device (not shown) of conventional self-lapping type located inthe pilots compartment of the plane serves to control-the supply of fluid underpressureto the pipe H.

With the piston valve 82 in its seated position as shown in Fig. 2, communication is established from the annular chamber '70 through aplurality of ports '52 tothe passage 69 and pipe l3. It willthus be apparent that fluid under pressure suppliedto the pipe li under the control of the brake controlling valve devicein the pilotscompartment may flow to the brake tube-Beto effect expansion thereof and a consequent application of force pressing th annular brake shoe 1 into frictional engagement with the inner surface of the brake drum 5, thereby effecting a brake application on wheel I. I

The tubular member connecting the piston BI and piston valve 62 is provided with one ormore ports 13 through which fluid under-pressuresupplied from the pipe ll to the annular chamber may flow'at a restricted rate to the interior of the tubular member and to the chamber within the bore 59 at the outer face of. the piston 6|,

The release valve 15 further comprises apilot valve M of the poppet type cooperating with a. valve seat bushing 15 secured in-a central bore 16 in the cover65. The pilot valve-'14 is provided with. a fluted stem which extends slidably 8 through the central .bore of thez'xzalve seatbuslii-ng l5v andztheendbf which projects beyondthe outer face of thecover plate 65. A plurality-of exhaust portsll' opening out of the interiorof the valveseat bushing and extending to theex: terior of the cover provide for the exhaustof fluid underpressure from the chamber on the outer face of the piston- 61 upon the unseating of the valve-14.-

Valve l4. =is yieldingly biased to a seated position on theinner end of the valve seat bushing '15, as .by a coil spring 18 interposed between a spring :retainer 19' and the valve. The spring retainer 118 has a flange, at one end which fits into a, recess on the inner face of the cover 65 and against which the one end of the spring presses to hold it in place. i

The operating lever 52 of release valve [-6 is of I -shape, having twoarms extending in opposite directions from the portion to whichtlie link rod 54 is connected, each of the arms having near the end thereof a slot 80 through which a suitable. pin or lug 8| attached to the casing 58 extends. Two similar springs 82 and 83 are provided for exerting a spring force on the ends of the arms of the operating lever 52-respectively: to bias it to a central normal position, as shown in Fig. 2, wherein'a boss or contact surface 84 on the lever 'disengages the end.of"'the fluted stem of thepilotvalveld to allow seating of the pilot valve 14. The tension of the springs 82- and 83 may be adjusted to provide more-or less force, as desired, by means of adjusting'nuts 85. Nuts 85- have smooth portions fitted into and rotatable in bores 86 in these-sing 5 8, which nuts when turned shift cooperating screws 81 having spring seats 88 secured thereto in which one end-of each of the springs 82 and 83 is res ceivedl' Suitable annular spring seats 89 may alsobeprovidedat the ends of the crossarmsof lever 52, as shown, for receiving the opposite ends of the-springs 82 and 83 respectively. Itwill thus be seen that springs 82 and 83 may beindividually adjusted to determine-the amount of force required to rotarily shift the flange-35 of the rotary inertia device l5 from its normal position for the purpose of unseating thepilot valve 14 and therebyeffect the unseating of the piston valve 62 in the manner here'- inafter to" be described; Springs 82 and 83-.-are so tensioned thatnnseating of the valve 144s effected whenever the torque force exerted on flange 35 exceeds a certain value occurring in response to deceleration and acceleration ofthe landing wheel and casing H at an excessive rate occurring only incident to a wheel slip condition. ltlwill' be apparent also that the flange 35 is maintained in its certain non-rotative normal position by the action of the springs 82 and 83 actingthrough the lever 52, the link 54, the rocker arm.53- and the operating rod 40.

While, for simplicity, only one landingwheel assembly is shown in the drawings, it should-be understood that each landing wheel of an airplane is intended to be similarly provided with a rotary inertia device l5- and releasevalve I6 and to be controlled in the manner now to bedescribed for the one landing wheel shown.

In operation, let it be assumed that an airplanehaving'the landing wheel i is comingin fora landing and that the tireon wheel l contacts the runway orground surface. Wheel l and consequently the casing llof the rotary celeratedtoward a rotational speed corresponding to the ground speed of the airplane. Let it be assumed that rotation of the wheel in the forward direction corresponds to rotation of the casing H in a counter-clockwise direction, as seen in Fig. 4. The latches 41 engage one or more lugs on the clutch member 42 and lock the clutch member for rotation with the casing. The orbit gear 29 is thus impelled to rotate with the casing H by the frictional force exerted thereon by the two clutch rings 4| and 43. If the driving force or torque exceeds the limit of the friction of the two clutch rings 4| and 43, the orbit gear 29 will slip with respect to the casing thus limiting the amount of torque force which may be exerted to accelerate the flywheel 22 to a degree corresponding to the frictional force exerted, and preventing damage to the parts of the mechanism, especially the teeth of planetary gears 3| and orbit gear 29.

Due to the reactive forces on the flange 35 by reason of the tendency of the flywheel 22 to lag behind the orbit gear 29, the flange 35 is rotationally urged out of its normal position to effect a corresponding rotational urge on the operating rod 40. Under the assumed circumstances, the flange 35 will be urged in a counterclockwise direction, as seen in Fig. 4, and the operating rod 40 and the rocker arm 53 will be correspondingly urged rotationally in a clockwise direction, as viewed in Fig. 2, thus exerting a push on the link rod 54 and rocking the lever 52 of the release valve l6 correspondingly in a clockwise direction about the right-hand pin 8| against the resisting force of the spring 82 to effect unseating of the pilot valve 14 of the release valve.

If the pilot of the airplane operates the brake controlling valve device in his compartment to cause fluid under pressure to be supplied through the pipe promptly after the tires of the landing wheels contact the runway and while the pilot valve 14 is unseated in the manner just described, the pressure of the fluid thus supplied into the chamber 10 of the release valve device will be effective to shift the piston valve device 60 from the position in which it is shown in Fig. 2 to the position in which the piston 6| engages the cover 65. This occurs because of the differential of fluid pressure established on the piston valve device 60 by reason of the exhaust of fluid under pressure from the interior of the tubular portion of the piston valve device resulting from unseating of the pilot valve 14, the port 13 in the tubular portion of the piston valve device 60 being sufiiciently small in flow area that the flow of fiuid under pressure therethrough from chamber 10 is insufficient to equalize the fluid pressures on opposite sides of the piston 6|.

Piston valve 62 will thus be unseated from the annular rib seat 61 and shifted past the ports -12, so as to establish communication from the pipe I 3 and the brake tube 8 connected thereto to the atmospheric exhaust passage 68, and at the same time to cut ofl communication from the chamber 10 to the passage 69, thereby preventing the supply of fluid under pressure to the brake tube 8 and releasing fluid under pressure, if any there be, from the brake tube 8. Application of the brake on the landing wheel is thus prevented.

After a suflicient interval of time elapses for the flywheel 22 of the rotary inertia device to be accelerated substantially to the rotational speed of the casing H, the reactive forces exerted on the flange 35 will diminish and consequentlythe.

spring 82 will act to return the operating lever 52 of the release valve IE to its normal central position in which the pilot valve 14 is seated. Upon the reseating of the pilot valve 14 the fluid pressures on opposite sides of the piston 6| are rapid- 1y equalized through the port 13, with the result that the force of the spring 64 and the difierential fluid pressure acting on the outer face of the piston 6| shifts piston valve device 60 back to its normal position, in which it is shown in Fig. 2. Communication is thus reestablished from the pipe H to the pipe |3. Consequently, fluid under pressure is supplied to the brake tube 8 to effect an application of the brake shoe 1 in accordance with the pressure of the fluid supplied under the control of the brake controlling valve device in the pilots compartment.

It will. thus be seen that it is unnecessary for the pilot to delay effecting an application of the brakes following the instant the landing wheels first contact the runway because, as hereinbefore described, the release valve I6 is automatically controlled to prevent the supply of fluid under pressure to the brake tube 8 and the consequent brake application until inertia element or flywheel 22 of the rotary inertia device is accelerated substantially to the rotational speed of the landing wheel to render it effective for subsequent control of the brakes in the manner now to be described.

Let it now be asumed that with a brake application initiated in the manner previously described, the fluctuation of the load on the landing wheels of the airplane or the bouncing of the airplane so reduces the'adhesion between the tires of the wheels and the runway that the brake application is effective to cause rotative deceleration of the landing wheels at a rapid rate characteristic of wheel slippage.

Due to the excessively rapid rate of deceleration of the landing wheel I and consequently of the casing H, as the landing wheel begins to slip, the casing tends to decelerate the orbit gear 29' correspondingly. However, in this case, the frictional force holding the orbit gear to the casing is limited by the frictional force exerted by the single clutch ring 4|, because by reason of the tendency of the casing I! to rotate at a slower speed than the orbit gear 29 the latches 41 slip over the lugs 5| on the clutch member 42 and consequently the clutch ring 43 is ineffective to exert a frictional retarding force on the orbit gear 29. Thus, the casing I! will slip with respect to the orbit gear 29 so long as the frictional force exerted between the casing l1 and the orbit gear 29 through the clutch ring 4| is exceeded. 7

At the same time due to the retardation of the orbit gear 29 and the tendency of the inertia element or flywheel 22 to overspeed the orbit gear, that is rotate faster than the normal rate of speed with respect to the orbit gear, the reactive forces developed on the flange 35 are such as to cause rotational shifting of the flange 35 out of its normal non-rotative position, in a clockwise di rection, as viewed in Fig. 4. A corresponding rotation of the operating rod 40 and rocker arm 53 in a counter-clockwise direction, as viewed in Fig. 2, will be effected, thereby exerting a pulling force on link rod 54 to cause the operating lever 52 of the release valve I6 to be rocked in a countar-clockwise direction, as seen in Fig. 2, about the left-hand pin 8| in opposition to the resistance of the coil spring 83 to effect. unseatin of the pilot valve-I4 of the release valve. The adjustment ofthe spring 83 issuch that as long;

as the landingwheeldeceleratesat a rapid. rate characteristic of slipping, pilot valve 74 will be maintained; unseated, Thus, as previously described, the unseating. of. pilot valve'i i while the supply of fluid. under pressure into the pipe ii is maintained under the control of. the brake controlling. valve device in the.- pilots compartment, eifects unseating of release valve 62 to cut off communication between the'pipe H and the pipe l3 and to establish communication between the pipe l3 and the exhaust passage 68. Fluid under pressure in the brake tube 8 is thereby released rapidly to atmosphere. to eflect a rapid reduction in the degree of the brake application effective on the landing wheel.

Due to' the prompt and rapid reduction of the braking force on the landing. wheel I as just described, the landing wheel' I- correspondingly ceases to decelerate and, by reason of its contact with the runway, again begins to accelerate back toward a speed corresponding to the ground speed of the airplane. At this time, by reason of the action. of the latches 4-1; the clutch member 42 is again locked for. rotation with the casing and, consequently, the frictional force exerted by both clutch rings 41- and 43 is eiiecti-ve to cause acceleration of the inertia element or flywheel 22. It will be seenthat the driving torque exerted to aceleratethe inertia element or flywheel 22 is thus limited to the higher degree determined by the higher degree of frictional force exerted by both the clutch rings 4i and 43, in comparison to the relatively lower limit of driving torque exerted. solely by the clutch ring H- during deceleration-of the casing ll.

It will be apparent that acceleration of the landing wheel and corresponding rotative acceleration of the casing 11' during this interval in which the landing wheel is slipping efiects a reversal of the reactive forces on the flange 35 from that in eiiect during deceleration; and thus the operating lever 52 of the release valve 16 is again rocked in opposition to the force of spring 82 in a clockwise direction, as viewed in Fig. 2, to effect and maintain the pilot valve 14 of the release valve unseated so long as the acceleration rate of the landing wheel is'sufficient to overcome the force of the spring 82. The momentary reseating of pilot valve 14 as the lever 52- of release valve device ['6 passes the normal position thereof in shifting from one side of that position to the other is insufficient to effect the position of release valve 62 at that time.

As the rotational speed of the landing wheel approaches synchronism with the ground speed of the airplane, the inertia element or' flywheel 22 of therotary inertia device will have accelerated corespondirigly so that the'reactive forces on the flange 35 will have reduced enough that spring 82 acts to restore the lever 52 to its normal position in which the pilot valve" is'reseated. Thus, as previously described, with the supply of fluid under pressure maintained into the pipe H from the brake controlling valve in the pilot's compartment, the piston valve device 88 will be instantly restored to its normal position, in which it is shown in Fig. 2, thus cutting 01f the exhaust of fluid under pressure from the brake tube 8 and restoring. the communication through which fluid under pressure is supplied from the pipe TI to the pipe [3 and the brake tube 8. Reapplication of the brake on the landing wheel is thus effected substantially at the time the landing wheel is synchronized with. t ground speed of the airplane.

It will beunderstood that by employing a brake controlling valve in the pl1'0t3s compartment of the self-lapping type, fluid at. a pressure determined by the position of the brake controlling. handle isalways available notwithstanding the venting of fluid under pressure from the brake tube. Consequently, the degree: of brake appli cation restored is always determined by the position of the operating handle of the brake con.- trolling valve device.

In the event that brake reapplication on the landing wheel again initiates a slipping condition of the wheel, the above operation will be repeated so that at no time are the landing wheels permitted to attain a locked orslipping: condition.

After'an airplane comes to a. stop following: the landing; the brakes maybe released at any time'iby simply restoring the brake controlling valve device in. the pilot's compartment to. its release position in which fluid under pressure is released from the brake tube 8 reversely through the pipe l3 and pipe 'II' and exhausted to atmosphere. at the brake controlling valve device. It will be seen that whenever the wheels of the airplane cease rotation due to stopping of the plane on the ground, no reactive forces remain on flange 35 and consequently springs 82 and 83 restore lever 52 to its'normal centered position, in which pilot valve 14 is seated. Thus piston valve 62 of the release valve device i6 is automatically restored to its normal seated position, in which it is shown in Fig. 2, thereby establishing the communication through which fluid under pressure may be supplied 'to or released from the brake tube 8 under the control of the brake controlling valve device operated by the pilot of the airplane.

Having now described my invention, what I claim as new and desire to secure by Letters Patent, is:

I. An inertia type wheel slip detector device comprising a rotative housing adapted to be rotated according to the rotation of a vehicle wheel,

I a rotative mass, torque transmission means for driving said mass from said rotative housing, said transmission means including a multiple clutch device one portion of which is in driving engagement at all times and another portion of which is in driving engagement only when the rotation of said mass is accelerated.

2. An inertia type wheel slip detector device comprising a rotative housing adapted to be rotated according to the rotation of a vehicle Wheel, a rotative mass, power transmission means for driving said mass from said rotative housing, said power transmission means including a dual friction type clutch, one clutch portion of which is in driving engagement at all times and a second clutch portion of which is in driving engage.- ment only when the rotation of said massis ac.- celerated, and adjustable means for selectively causing said second portion of said clutch to be actuable into driving engagement for one direction of rotation of said housing or for the op-.

posite direction of rotation of said housing.

3. A control mechanism comprising a rotary housing, a rotary inertia mass enclosed in said housing, power transmission -means for operatively connecting said housing to said inertia mass for accelerating and decelerating said massv to rotative speeds corresponding to the rotatlve speed of said housing, said transmission means" including an orbit gear rotatively mounted in said housing, clutch means for frictionally associating said orbit gear and said housing for rotatlon'together, gear mechanism meshing with said orbit tion of the housing and for limiting to a different degree the frictional force applied by said clutch means to hold said orbit gear againstrotation with respect to said housing upon deceleration of said housing;

4. A control mechanism comprising a rotary housing, a rotary inertia mass enclosed in said housing, power transmission means for operatively connecting said housing to said inertia mass for accelerating and decelerating said mass to rotative speeds corresponding to the rotative speed of said housing, said transmission means including an orbit gear rotatably carried in said housing, two clutch members, resilient means active to bias said clutch members into frictional contact with said orbit gear, one of said clutch members frictionally engaging the housing at all times and. being constantly effective to transmit a driving force from said housing to drive said orbit gear, and means for locking the other of said clutch members to said housing upon relative movement of the orbit gear and housing occurring as an incident to the acceleration of the housing.

5. A control mechanism comprising a rotary housing, a rotary inertia mass enclosed in said housing, power transmission means for operatively connecting said housing to said inertia mass for accelerating and decelerating said mass to rotative speeds corresponding to the rotative speed of said housing, said transmission means including an orbit gear carried in said housing, a clutch member interposed between the housing and the orbit gear effective to transmit driving force from said housing to accelerate or to retard said orbit gear, and auxiliary clutch means effective only to transmit a driving force from said housing to accelerate said orbit gear.

6. A control mechanism comprising a rotary housing, a rotary inertia mass enclosed in said housing, power transmission means for operatively connecting said housing, to said inertia mass for accelerating and decelerating said mass to rotative speeds corresponding to the rotative speed of said housing, said transmission means includin an orbit gear carried in said housing, two annular clutch members carried by the housing and frictionally engaging opposite sides of said orbit gear, one of said clutch members having peripheral projections, a cover adapted to be secured to said housing in either of two reversed positions, and latch means carried by said cover and biased to engage the projections on said one of the clutch members whereby to provide a positive lock for driving said clutch member from said housing only in one direction of rotation of the housing with said cover in one position and a positive lock for driving said clutch member from said housing only in the opposite direction of rotation of the housing with the said cover in the other of its said two positions.

'7. A control mechanism comprising a rotary housing, a rotary inertia mass enclosed in said housing, power transmission means for operatively connecting said housin to said inertia mass for accelerating and decelerating said mass to rotative speeds corresponding to the rotative speed correspondingto the rotative speed of said housing, said transmission means including an orbit gear carried in said housing, two annular clutch members carried by said housing and frictionally engaging opposite sides respectively of said orbit gear, resilient means effective to cause both clutch members to continuously engage said orbit gear, one of said clutch members being continuously effective to drive said orbit gear from said housing, the other of said clutch members having a latching surface, a latch normally biased to engage the latching surface of said clutch member whereby to provide a positive lock for driving said clutch member from said housing upon acceleration of the housing and free rotation of the housing relative to said clutch member upon deceleration of the housing.

8. A control mechanism comprising a rotary housing, a rotary inertia mass enclosed in said housing, power transmission means for operatively connecting said housing to said inertia mass for accelerating and decelerating said mass to rotative speeds corresponding to the rotative speed of said housing, said transmission means including an orbit gear carried in said housing, clutch means comprising an annular clutch member on each side of said orbit gear, resilient means active to bias said annular clutch members into frictional contact with said orbit gear,

one of said annular clutch members engaging the housing at all times and being effective to drive said mass, means operative as an incident to acceleration of said housing for locking the other of said clutch members to said housing to cause the said other clutch member to rotate with the housing and being ineffective to lock said other of said clutch members to the housing upon deceleration of said housing.

9. A control mechanism comprising a rotary housing, a rotary inertia mass enclosed in said housing, an orbit gear rotatively carried in said housing, a first annular clutch member frictionally cooperating with the housing and one side of said orbit gear, a second clutch member frictionally cooperating with the other side of said orbit gear, resilient means active to bias said annular clutch members into frictional engagement with their respective sides of said orbit gear and also to bias said first clutch member into frictional contact with the said housing, means operative upon acceleration of said housing for locking the said second clutch member for rotation with said housing and operative upon deceleration of said housing for unlocking said second clutch member from said housing to permit relative rotary movement therebetween, a plurality of planetary gears cooperating with said orbit gear and arranged to drive said inertia mass upon rotation of the orbit gear, rotary means supported in said housing for carrying said planetary gears, resilient means biasing said rotary member to a normal non-rotative position and yieldable responsively to the reactive forces exerted on the rotary member incident to acceleration or deceleration of the housing to permit rotary movement of the rotary member to one or the other side of said normal position, and control means actuated responsively to rotary displacement of the rotary member out of its normal position.

10. An inertiatype wheel slip detector device comprising, in combination, a rotative housing, a rotative inertia mass, and transmission means for transmitting a driving force from said housing to said mass, said transmission means in- 15 eluding a'first drive means efiective at'all times to transmit an accelerating or decelerating force from-saidhousingto said mass and a second drive means eifective only to transmit an accelerating force'from said housing to said mass.

113 An inertia type wheel slip detectordevice comprising, in combination, a rotative housing, a rotative inertia mass,'and transmission means for transmitting a driving force from said housing to said mass, said transmission means including a first drive means effective at all times to transmit an accelerating or decelerating force from said housing to said mass, a second drive means and means effective to cause said second 16 drive means to be effective only to transmit an accelerating force from said housing to said mass.

RANKIN J. BUSH.

REFERENCES CITED The'following references are of record in the file or this patent:

UNITED STATES PATENTS 

